EP4001693B1 - Reibrohre - Google Patents

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Publication number
EP4001693B1
EP4001693B1 EP21209659.8A EP21209659A EP4001693B1 EP 4001693 B1 EP4001693 B1 EP 4001693B1 EP 21209659 A EP21209659 A EP 21209659A EP 4001693 B1 EP4001693 B1 EP 4001693B1
Authority
EP
European Patent Office
Prior art keywords
carrying shaft
torque carrying
torque
friction tube
shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP21209659.8A
Other languages
English (en)
French (fr)
Other versions
EP4001693A3 (de
EP4001693A2 (de
Inventor
Aaron COOLING
Glenn C. Lemmers Jr.
David S. Behling
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hamilton Sundstrand Corp
Original Assignee
Hamilton Sundstrand Corp
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Filing date
Publication date
Application filed by Hamilton Sundstrand Corp filed Critical Hamilton Sundstrand Corp
Publication of EP4001693A2 publication Critical patent/EP4001693A2/de
Publication of EP4001693A3 publication Critical patent/EP4001693A3/de
Application granted granted Critical
Publication of EP4001693B1 publication Critical patent/EP4001693B1/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/129—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon characterised by friction-damping means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
    • F16D3/14—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions combined with a friction coupling for damping vibration or absorbing shock
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
    • F16D7/02—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type
    • F16D7/024—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type with axially applied torque limiting friction surfaces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F7/00—Vibration-dampers; Shock-absorbers
    • F16F7/02—Vibration-dampers; Shock-absorbers with relatively-rotatable friction surfaces that are pressed together
    • F16F7/04—Vibration-dampers; Shock-absorbers with relatively-rotatable friction surfaces that are pressed together in the direction of the axis of rotation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/02—Shafts; Axles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/22—Vibration damping

Definitions

  • the present invention relates to torque bearing shafts, and more particularly to dampening for torque bearing shafts.
  • Torsion shafts can undergo vibration which can limit the useable life of the torsion shafts.
  • the vibrations are those that act in the angular or circumferential direction.
  • a torsion shaft must be designed to have enough mass to handle the angular vibrations for the entire useable life of the torsion shaft.
  • Torsion shafts are disclosed in US 2016/097420 .
  • a torsion shaft assembly includes a torque carrying shaft including a driven end configured for receiving torque input to the torque carrying shaft and a driving end configured for outputting torque output from the toque carrying shaft.
  • the torque carrying shaft includes an axial facing damping interface surface axially between the driven end and the driving end.
  • a friction tube is disposed outboard of the torque carrying shaft. The friction tube is connected at a first axial location to be driven by the torque carrying shaft.
  • the friction tube includes an axial facing damping interface surface that abuts the axial facing damping interface surface of the torque carrying shaft, forming a damping interface to provide frictional dampening against angular vibrations occurring as differential angular displacement between the driven end and the driving end of the torque carrying shaft.
  • the torque carrying shaft is hollow defining a fluid passage therethrough.
  • a helical spring can be engaged with the friction tube on a driven end of the friction tube to bias the friction tube toward the damping interface.
  • the friction tube can be engaged with drive flats of the torque carrying shaft.
  • the drive flats of the torque carrying shaft can be more proximate the driven end of the torque carrying shaft than to the driving end.
  • the torque carrying shaft and the friction tube can be at least ten times longer than a distance from the driven end of the torque carrying shaft to the drive flats taken in an axial direction.
  • the drive flats of the torque carrying shaft can be defined as facets in a radially extending flange of the torque carrying shaft.
  • the axial facing damping interface surface of the torque carrying shaft can be defined on a radially extending flange of the torque carrying shaft.
  • the radially extending flange can be more proximate the driving end than the driven end.
  • the torque carrying shaft and the friction tube can be at least ten times longer than a distance from the driving end of the torque carrying shaft to the radially extending flange taken in an axial direction.
  • the torque carrying shaft can include one or more bores defined radially therethrough from the fluid passage to an annular space between the torque carrying shaft and the friction tube for passage of fluids between the fluid passage and the annular space.
  • the friction tube can include one or more bores defined radially therethrough from the annular space to an exterior of the friction tube for passage of fluids between the annular space and the exterior.
  • FIG. 1 a partial view of an embodiment of a torsion shaft assembly in accordance with the present invention is shown in Fig. 1 and is designated generally by reference character 100.
  • FIGs. 2-3 Other embodiments of systems in accordance with the disclosure, or aspects thereof, are provided in Figs. 2-3 , as will be described.
  • the systems and methods described herein can be used to dampen angular vibration in torque shafts.
  • a torsion shaft assembly 100 includes a torque carrying shaft 102 including a driving end 106 configured for receiving torque input to the torque carrying shaft 102 and a driven end 104 configured for outputting torque output from the toque carrying shaft 102.
  • the torque carrying shaft 102 includes an axial facing damping interface surface 108 (labeled in Fig. 3 ) axially between the driven end 104 and the driving end 106.
  • a friction tube 110 is disposed outboard of the torque carrying shaft 102. The friction tube 110 is connected at a first axial location 112 to be driven by the torque carrying shaft 102.
  • the friction tube 110 includes an axial facing damping interface surface 114 that abuts the axial facing damping interface surface 108 of the torque carrying shaft 102, forming a damping interface 116 to provide frictional dampening against angular vibrations occurring as differential angular displacement about rotational axis A between the driven end 104 and the driving end 106 of the torque carrying shaft 102.
  • a helical spring 118 can be engaged with the friction tube 110 on the driven end 104 of the friction tube 110 to bias the friction tube 110 toward the damping interface 116 of Fig. 3 , i.e. pushing the friction tube 110 to the right along the rotational axis A as oriented in Fig. 2 .
  • the friction tube 110 is engaged with drive flats 120 of the toque carrying shaft 102.
  • the drive flats 120 of the torque carrying shaft 102 are more proximate the driven end 104 of the torque carrying shaft 102 than to the driving end 106.
  • the torque carrying shaft 102 and the friction tube 110 are at least ten times longer (in the axial direction of the rotational axis A) than a distance D1 from the driven end 104 of the torque carrying shaft 102 to the drive flats 120.
  • the drive flats 120 of the torque carrying shaft 102 are defined as facets in a radially extending flange 122 of the torque carrying shaft 102.
  • the axial facing damping interface surface 108 of the torque carrying shaft 102 is defined on a radially extending flange 124 of the torque carrying shaft 102.
  • the radially extending flange 124 is more proximate the driving end 106 than the driven end 104 (each end 106, 104 is shown in Fig. 1 ).
  • the torque carrying shaft 102 and the friction tube 110 are at least ten times longer than a distance D2 from the driving end 106 of the torque carrying shaft 102 to the radially extending flange 124 taken in the axial direction.
  • Torsion shafts with vibration dampening as disclosed herein can be reduced in mass and still manage the same loads and useful life time as more massive traditional torsion shafts without such dampening.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Springs (AREA)
  • Vibration Prevention Devices (AREA)

Claims (14)

  1. Torsionswellenbaugruppe, umfassend:
    eine drehmomenttragende Welle (102), die ein angetriebenes Ende (104), das konfiguriert ist, um ein Eingangsdrehmoment der drehmomenttragenden Welle aufzunehmen, und ein antreibendes Ende (106) beinhaltet, das konfiguriert ist, um ein Ausgangsdrehmoment von der drehmomenttragenden Welle auszugeben, wobei die drehmomenttragende Welle eine axial zugewandte Dämpfungsschnittstellenfläche (108) axial zwischen dem angetriebenen Ende und dem antreibenden Ende beinhaltet; und
    ein Reibrohr (110), das außerhalb der drehmomenttragenden Welle angeordnet ist, wobei das Reibrohr an einer ersten axialen Stelle verbunden ist, um von der drehmomenttragenden Welle angetrieben zu werden, und wobei das Reibrohr eine axial zugewandte Dämpfungsschnittstellenfläche (114) beinhaltet, die an der axial zugewandten Dämpfungsschnittstellenfläche der drehmomenttragenden Welle anliegt, wobei eine Dämpfungsschnittstelle (116) gebildet wird, um eine Reibdämpfung gegen Winkel vibrationen bereitzustellen, die als unterschiedliche Winkelverschiebung zwischen dem angetriebenen Ende und dem antreibenden Ende der drehmomenttragenden Welle auftreten; und
    dadurch gekennzeichnet, dass:
    die drehmomenttragende Welle (102) hohl ist, wobei ein Fluiddurchgang durch sie hindurch definiert wird.
  2. Torsionswellenbaugruppe nach Anspruch 1, ferner umfassend eine Schraubenfeder (118), die mit dem Reibrohr in Eingriff steht, um das Reibrohr gegen die Dämpfungsschnittstelle vorzuspannen.
  3. Torsionswellenbaugruppe nach Anspruch 1, wobei das Reibrohr mit Antriebsflächen (120) der drehmomenttragenden Welle in Eingriff steht.
  4. Torsionswellenbaugruppe nach Anspruch 3, wobei die Antriebsflächen (120) der drehmomenttragenden Welle näher an dem angetriebenen Ende (104) der drehmomenttragenden Welle liegen als an dem antreibenden Ende (106).
  5. Torsionswellenbaugruppe nach Anspruch 3, wobei die Antriebsflächen der drehmomenttragenden Welle als Facetten in einem sich radial erstreckenden Flansch (124) der drehmomenttragenden Welle definiert sind.
  6. Torsionswellenbaugruppe nach Anspruch 3, wobei die drehmomenttragende Welle (102) und das Reibrohr (110) mindestens zehnmal länger sind als der Abstand zwischen dem angetriebenen Ende der drehmomenttragenden Welle und den Antriebsflächen, gesehen in einer axialen Richtung.
  7. Torsionswellenbaugruppe nach Anspruch 1, wobei die axial zugewandte Dämpfungsschnittstellenfläche der drehmomenttragenden Welle auf einem sich radial erstreckenden Flansch (124) der drehmomenttragenden Welle definiert ist.
  8. Torsionswellenbaugruppe nach Anspruch 7, wobei der sich radial erstreckende Flansch näher an dem angetriebenen Ende liegt als an dem antreibenden Ende.
  9. Torsionswellenbaugruppe nach Anspruch 8, wobei die drehmomenttragende Welle (102) und das Reibrohr (110) mindestens zehnmal länger sind als der Abstand zwischen dem antreibenden Ende der drehmomenttragenden Welle und dem sich radial erstreckenden Flansch, gesehen in einer axialen Richtung.
  10. Torsionswellenbaugruppe nach einem der vorhergehenden Ansprüche, wobei die drehmomenttragende Welle eine oder mehrere Bohrungen (128) beinhaltet, die radial durch ihn hindurch von dem Fluiddurchgang (126) zu einem ringförmigen Raum (130) zwischen der drehmomenttragenden Welle und dem Reibrohr für den Durchgang von Fluiden zwischen dem Fluiddurchgang und dem ringförmigen Raum definiert sind.
  11. Torsionswellenbaugruppe nach Anspruch 10, wobei das Reibrohr eine oder mehrere Bohrungen (132) beinhaltet, die radial durch ihn hindurch von dem ringförmigen Raum zu einer Außenseite des Reibrohrs für den Durchgang von Fluiden zwischen dem ringförmigen Raum und der Außenseite (134) definiert sind.
  12. Torsionswellenbaugruppe nach Anspruch 1, wobei das Reibrohr (110) mit Antriebsflächen (120) der drehmomenttragenden Welle in Eingriff steht, wobei die Antriebsflächen der drehmomenttragenden Welle als Facetten in einem ersten, sich radial erstreckenden Flansch (124) der drehmomenttragenden Welle definiert sind, wobei die axial zugewandte Dämpfungsschnittstellenfläche (108) der drehmomenttragenden Welle auf einem zweiten, sich radial erstreckenden Flansch der drehmomenttragenden Welle definiert ist.
  13. Torsionswellenbaugruppe nach Anspruch 12, ferner umfassend eine Schraubenfeder (118), die mit dem Reibrohr an einem angetriebenen Ende des Reibrohrs in Eingriff steht, um das Reibrohr gegen die Dämpfungsschnittstelle vorzuspannen.
  14. Torsionswellenbaugruppe nach Anspruch 12, wobei die drehmomenttragende Welle und das Reibrohr mindestens zehnmal länger sind als der Abstand zwischen dem angetriebenen Ende der drehmomenttragenden Welle und den Antriebsflächen, gesehen in einer axialen Richtung, und mindestens zehnmal länger sind als der Abstand zwischen dem antreibenden Ende der drehmomenttragenden Welle und dem sich radial erstreckenden Flansch, gesehen in einer axialen Richtung.
EP21209659.8A 2020-11-20 2021-11-22 Reibrohre Active EP4001693B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US16/953,723 US11320022B1 (en) 2020-11-20 2020-11-20 Friction tubes

Publications (3)

Publication Number Publication Date
EP4001693A2 EP4001693A2 (de) 2022-05-25
EP4001693A3 EP4001693A3 (de) 2022-06-01
EP4001693B1 true EP4001693B1 (de) 2024-05-08

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EP (1) EP4001693B1 (de)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11320022B1 (en) * 2020-11-20 2022-05-03 Hamilton Sundstrand Corporation Friction tubes
US20230358175A1 (en) * 2022-05-04 2023-11-09 Hamilton Sundstrand Corporation Thrust damper for a shaft in an aircraft

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4411637A (en) * 1981-12-17 1983-10-25 The Bendix Corporation Compliantly mounted damping means
US4605386A (en) 1985-08-19 1986-08-12 Harris Gerald R Compact variable speed pulley assembly
DE3740756A1 (de) 1987-12-02 1989-06-22 Loehr & Bromkamp Gmbh Drehelastische hohlwelle
US6702076B2 (en) 2001-01-16 2004-03-09 Michael T. Koleda Shaft vibration damping system
WO2003013793A1 (en) 2001-08-10 2003-02-20 American Tool Companies, Inc. Increased and variable force and multi-speed clamps
US7214135B2 (en) 2003-08-29 2007-05-08 Torque-Traction Technologies, Llc Drive shaft having a damper insert
DE102005032499B4 (de) 2004-07-13 2009-10-22 Lg Electronics Inc. Dämpfer zur Vibrationsdämpfung und damit ausgerüstete Waschmaschine
US20060276250A1 (en) 2005-06-07 2006-12-07 Caraustar Industries, Inc. Drive Shaft Damper Blank
DE202006017587U1 (de) 2006-11-17 2007-01-18 Dieter Hölzle Technik-Projekte GmbH Drehdämpfer
WO2011039817A1 (ja) 2009-10-01 2011-04-07 トヨタ自動車株式会社 回転軸の振動減衰機構
AT510239B1 (de) 2010-07-29 2012-09-15 Andritz Ag Maschf Einrichtung zur dämpfung von schwingungen in einem antriebsstrang
DE102014207724A1 (de) 2013-04-30 2014-10-30 Schaeffler Technologies Gmbh & Co. Kg Schwingungsdämpfer
US9416815B2 (en) 2014-10-01 2016-08-16 GM Global Technology Operations LLC Driveshaft with two-stage stiffness
US10054167B2 (en) 2014-10-01 2018-08-21 GM Global Technology Operations LLC Driveshaft with two-stage stiffness
US11320022B1 (en) * 2020-11-20 2022-05-03 Hamilton Sundstrand Corporation Friction tubes

Also Published As

Publication number Publication date
US11320022B1 (en) 2022-05-03
US20220163091A1 (en) 2022-05-26
EP4001693A3 (de) 2022-06-01
US20220163092A1 (en) 2022-05-26
US11703105B2 (en) 2023-07-18
EP4001693A2 (de) 2022-05-25

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